Hydraulic steering mechanism



.Fume 2, i953 E. A. PUERNER 640,322

HYDRAULIC STEERING MECHANISM Filed Jan. 2, 1951 2 sheets-'sheet 1 "www Hump.

25 INVENTOR.

3/47 3249 3l /'ga' BY @Wh/MM June 2, E953 E. A. PUERNER 2,540,322

HYDRAULIC STEERING MECHANISM Filed Jan. 2, 1951 2 Sheets-Sheet 2 Patented June 2, 1953 HYDRAULIC STEERING MECHANISM Erving A. Puerner, Milwaukee, Wis., assigner to Shallcross Controls, Inc., Milwaukee, Wis., a corporation of Wisconsin Application January 2, 1951, Serial No. 203,915

19 Claims.

This invention relates to improvements in hydraulic steering mechanisms.

There have been a number of hydraulic steering mechanisms developed heretofore, but not any of these has been entirely satisfactory. Many of the prior hydraulic steering mechanisms have incorporated therein a four-way type valve for controlling the movements of a double acting piston. The conventional four-way valves have relatively movable parts therein formed with ports or grooves which are moved into and out of registration. Due to the fact that during movement of these parts, fluid under high pressure is caused to move through partially opened apertures or grooves therein, wire drawing or erosion of the margins of said grooves or apertures results. This greatly reduces the life of the valve. A common method of reducing the expense of wire drawing is to construct the valve in a manner such that the more expensive parts of the valve are made of the hardest metal and the more cheaply manufactured parts thereof are made of softer metal so that the wear will occur on the latter parts.

Another disadvantage of prior hydraulic steering mechanisms is that upon failure of the fluid pressure the system is locked against movement due to the entrapment of hydraulic fluid in the cylinder which prevents movement of the piston. This, of course, prevents any steering of the vehicle. The potential dangers of such a mechanism are obvious.

l Another objection to prior steering mechanisms is the fact that said mechanisms fail to transmit to the driver any road feel or resistance which the steering mechanism encounters due to road conditions or the like in making a turn.-

Another disadvantage of certain of the prior steering mechanisms is the fact that the steering wheel and its shaft move axially when turned. This makes mounting of the steering worm on thrust bearings difficult and expensive.

With the above in mind, it is a principal object of the present invention to provide an improved hydraulic steering mechanism which is so constructed that if, for any reason, the duid pressure should fail, the vehicle in which said mechanism is embodied can still be driven manually.Y

A further object of the invention is to provide an improved hydraulic steering mechanism having embodied therein ball type valves which providev a large opening for a relatively small amount of movement off the valve seat and thereby substantially entirely avoid wire drawing of the valve parts.

A further object of the invention is to provide an improved hydraulic steering mechanism of the class described provided with means for transmitting road feel to the driver through the steering wheel, said mechanism also being constructed in such a manner that there is no axial movement of the steering wheel or its shaft at any time.

A further object of the invention is to provide an improved hydraulic steering mechanism which is simple in construction and which is inexpensive to manufacture because no special tooling is required therefor.

A further object of the invention is to provide an improved valve and pumping system which is adapted for use with most types of hydraulic steering gears and to provide an improved hydraulic steering mechanism which is connectible to the steering column of any manual steering mechanism to provide power steering therefor.

A further object of the invention is to provide an improved hydraulic steering mechanism of the class described which is strong and durable, which is compact, and which is otherwise well adapted for the purposes described.

With the above and other objects in view, the invention consists of the improved hydraulic steering mechanism and all of its parts and combinations as set forth in the claims andv all equivalents thereof.

In the drawing accompanying and forming a part of this specication, wherein are shown several embodiments of the invention, and wherein like characters of reference indicate the same parts in all of the views:

Fig. 1 is a fragmentary side elevational view of the improved hydraulicvsteering mechanism, parts being broken away and shown in section;

Fig. 2 is a longitudinal vertical sectional view taken approximately along the line 2-2 of Fig. 1;

Fig. 3 is a transverse vertical sectional View taken :along the line 3 3 of Fig. 1;

Fig. 4 is a fragmentary diagrammatic view of an alternative form of pumping arrangement;

Fig. 5 is a fragmentary side elevational view of a modified form of the invention, parts being broken away and shown in section; and

Fig. 6A is a transverse vertical sectional view taken along the line 6-6 of Fig. 5'.

Referring more particularly to Fig. 1 of the drawing the numeral l0 indicates` an enclosed gear casing provided internally with av pair of spaced coaxial bearings Il and l2. A shaft I3 3 is rotatably mounted in the bearings II and I2 and is formed between said bearings with a worm gear I4 having a relatively steep pitch. The worm gear I4 is formed at its opposite ends with parallel annular end faces which abut the inner ends of the bearings I! and I2 to prevent axial movement of the shaft I3.

A shaft I5 extends transversely within the casing I6 and is rotatably mounted in suitable bearings (not shown). The shaft I5 extends exteriorly of the casing I6, and keyed or otherwise fixed to said shaft exteriorly of the casing is a pitman arm I6. The arm I6 is pivotally connected to a linkage I'. which may be dirigibly connected to the front wheels of a vehicle. Within the casing IB a lever I8 is keyed intermediate its length onto the shaft I5, as shown, and is movable in a plane parallel with the axis of the shaft I3. The lever I8 has one end positioned adjacent the worm I4 and has formed on said end portion a frusto conical lug I9 which projects toward the worm I4 and ts between a pair of adjacent convolutions thereof to act as a cam follower in a manner well known in the art when driven by the worm. The pitch of the worm is such, however, that said worm can be rotated by movement of the lug i9 axially of said worm. Mounted on the casing ID is an hydraulic ram 2c having a cylinder 2 I in which a piston 22 having a piston rod 23 is reciprocatably mounted. The piston rod 23 is parallel with the shaft I3 and slidably extends through the wall of the casing Ill. The end of the piston rod within the casing IB is provided with a cross head 24 which is formed with a rectangular groove 25 to receive a wheel or roller 26 which is rotatably connected to the end of the lever I8 opposite the lug I9.

Mounted on the exterior of the housing i5 coaxially with the shaft I3 is a cylindrical control housing 2l. The adjacent end of the shaft I3 extends rotatably through the wall of the casing I0 and into the control housing 2l, as shown. A cylindrical valve block is positioned in the control housing 2l' and is formed at one end with a coaxial tubular extension 29 for non-rotatably receiving the end of the shaft i3. In the draw ing the shaft I3 is keyed to the tubular extension 29 by means of a key 30 (see Fig. 2). The valve block 28 is formed with a pair of spaced circumferential grooves 3l and 32 and is provided with sealing rings 33, 34 and 35 to provide a rotatable sealing connection between the valve block 25 and the control housing 2l at each side of each of the grooves 3| and 32.

In its end face opposite the sleeve 29- the con,- trol block 28 is formed with an axial cylindrical recess 36, and a sectoral portion 31 of the end of the control block radially outwardly oi the recess 36 is cut away, as shown in Figs. l and 3, to form axially extending shoulders or faces 38 and 39. The faces 38 and 39 preferably lie in planes which are parallel withy the axis of the block 28 and are disposed angularly with respect to each other, as shown. The faces 3e and 39 are respectively formed with `bores 4D and 4I to provide circular valve seats in said faces. The control block 28 is formed with a passage 42 which communicates between the bore 4c and the groove 3l as shown in Figs. l and 3. The block 28 is also formed with a passage 43 which communicates between the bore 4I and the groove 32.

The control block 28 is formed with an axial bore portion 44 (seeFig. 2) smaller than the recess 36 and with a second axial bore portion 45 of smaller diameter than the bore portion 44. An elongated torsion rod 46 has one end positioned in the bore portion and is fixed therein as by a tapered pin 4l extending transversely through the block 28 and said rod. A control sleeve 45, having an inside diameter slightly larger than the diameter of the rod 46, surrounds said rod and has an end portion of reduced outer diameter 49 rotatably positioned in the bore portion 44.

Formed on and extending radially outwardly from the portion 49 of the control sleeve 4B is a blade 58 which is normally positioned in the cutaway portion 3'? midway between the faces 3'8 and 35. The blade 56 is preferably enlarged adjacent its outer end as shown in Fig. 3. Positioned between the face 33 and the blade 50 is a ball 5l which is adapted to sealingly seat in the end of the bore 40 when pressed thereagainst by the blade 56. When the blade 50 is in its nor-l mal neutral position, however, the ball 5l, as shown in Fig. 3, is not so pressed and the bore 40 is in communication with the cutaway portion 3'I. A ball 52 is similarly positioned between the blade 5% and the open end of the bore 4I, said ball being adapted to seal the end of the bore 4I when pressed thereagainst by the blade 56. As shown in Fig. 3, the ball 52 is not sealingly pressed against theropen end of the bore 4I when the blade 56 is in neutral position, and the bore 4I communicates with the cutaway portion 3l when the blade is in neutral position.

The outer end wall of the control housing 21 is provided with an axial bearing sleeve 53 c l through which the control sleeve 43 rotatably extends. The sleeve 48 is formed with -a thrust collar 54 which abuts the inner end of the bearing 53 as shown. A steering wheel 55 is formed with an axial connecting sleeve 55, and the control sleeve 48 is formed at its outer end with a portion of reduced external diameter 5l which ts telescopically into the sleeve 56, as shown in Fig. 2. Outwardly of the bearing 53, the sleeve 56 and the outer ends of the control sleeve 48 and torsion rod 46 are xedly connected, as by the tapered pin 58 extending transversely therethrough, shown in Fig. 2.

A conduit 53 communicates through a suitable aperture in the control housing 2'I with the groove 3| of the valve block 28. The conduit 59 also communicates with one end of a conduit 66 which communicates at its other end with one end of the interior of the cylinder 2I. A conduit 6I communicates at one end with the opposite end of the interior of the cylinder 2I and also come municates with one end of a conduit 62,4 the other end of which communicates with the groove-32 of the valve block 28 through a suitable aperture in the control housing 2'I. The conduits 59 and 6I communicate with separate sources of nuid under pressure preferably in the nature of positive displacement pumps.

Fig. 1 shows an improved unitary pump assemblage providing two separate sources of fluid under pressure. A pump housing 63 has rotat-4 ably mounted therein threc gear type impellers 64, 65 and 66. The gear 65 may be suitably driven and meshes with the gears 64 and 66 to provide driving engagement therefor. It is apparent that rotation of the gears in the directions indicated provides pressure in chambers 6.1. and 68. The conduit 59 communicates with the pres.- sure chamber 61 as shown, and the conduit GIL communicates with the pressure chamber 68', as shown. It is obvious that by rotation of the gears in the directions indicated suction chambers 69 and 19 are also formed. A conduit 1I communicates between the suction chamber 69 .and a source of fluid or sump12, and a conduit 13 communicates between the suction chamber 19 and the sump 12, as shown. A return conduit 14 communicates between the outer end of the interior of the control housing 21 and the sump 12. An inlet check valve 80 connects the conduit 59 with the sump 12 and may do so via the conduit 1|, as shown. An inlet check valve 8| connects the conduit 6| with the sump 12, as shown.

Fig. 4 shows a modified form of pumpl arrangement, wherein two separate positive displacement pump .assemblages 15 and 16 are driven by a common shaft 11, the pump 15 drawing iiuid from the sump 12' through the conduit 13'k and discharging said fluid into the conduit 59'; and the pump 16 drawing fluid from the sump 12 through the conduit 1I and discharging said uid into the conduit 6I. In Fig. 4 the parts indicated by primed numerals are analogous to the parts indicated by the same unprimed numerals in Figs. 1 to 3. A conduit 82 provides communication between the sump 12 and a pair of inlet check valves Bll and 8l as shown, the valve 80 being connected to the conduit 59' and the valve 8| being connected to the conduit 6I'.

Operation With the parts in the positions shown in Figs. 1 and 3, fluid flows from the pressure chamber 61 through the conduit 59, the groove 3 I, the passage 42 and the bore 48, and flows freely from the mouth of the bore 49 into the interior of the control housing 21. This fluid flows back to the `sump 12 through the conduit 14. Because of the free flow of the. fluid along the path just described, no substantial pressures lare built up in the conduits 59 and 60 or cylinder 2 I. Similarly, iuid flows from the pressure chamber 68 through the conduits 6| and 62, the groove 32, the passage 43 and the bore 4| into the interior of the control housing 21. The fluid issuing from the mouth of the bore 4| also returns to the 'sump' 12, via the conduit 14. The free ow of the fluid through the path just described prevents a building up o-f any substantial pressures in the conduits 6| and 62 or in the cylinder 2|. Manual steering is accomplished by turning the wheel 55 to cause simultaneous rotation there-- with of the control sleeve 48, the torsion rod 46, the valve block 28 and the shaft I3. Rotation of the worm I4 with the shaft I3 moves the cam follower I9 and causes the lever I8, along with the shaft I5, to rotate. Rotation of the lever I8 causes movement o-f the crosshead 24 and of the piston 22, while rotation of the shaft I5 causes the pitman arm I6 to swing therewith in the same rotative direction to actuate the steering linkage I1 in a direction corresponding' to the direction of rotation of the hand wheel 55.

It will be noted that the torsion rod 46 is the only member which is flxedly connected to both the steering wheel 55 and the valve block 28. This rod is deformable and is made of material which will transmit a predetermined amount of rotational force from the wheel 55 to the valve block 28 without deformation. However, when the resistance to movement of the steering linkage I1 is such that the rotative force required to be applied to the worm I4 to overcome said resistance and move said linkage is in excess of the predetermined force which the rod 46 can withstand without deformation, turning of the wheel 55 in a clockwise direction as viewed from thek right of Fig. 1, will cause deformation or twisting of the rod 46.A As the rod 46 so twists, the sleeve 48 'and the blade 50 rotate with the wheel in a clockwise' direction relative to the valveblock 28.

Referring to Fig. 3, rotation of the blade 50 in a clockwise direction causes said blade to press the ball 5| onto its seat in the mouth of the bore 46. This forms a direct ydriving connection between the wheel 55 and the valve block 28, it being apparent that the rod 46 provides aspring load which tends to return the blade 50 to its normal neutral position. A lost motion connection between the sleeve 48 and the valve block 28 is provided by the blade 50 and balls 5| and 52 positioned between the faces 38 and 39.

When the bali 5I is pressed onto its seat by the blade 50, the fluid from the conduit 59 can no longer escape into the housing 21 through the borev 49, and as a result the fluid from the pressure chamber 61 flows through the conduits 59 and 5 0 into the cylinder 2| at the left hand side of the piston 22. This causes the piston 22 to immediately move toward the right and to pull with it the piston rod 23 and crosshead 24. Movement of the crosshead 24 to the right causes clockwise rotation of the lever I8 and clockwise swinging movement of the pitman arm I6, which in turn causes movement toward the left of the linkage I'I. Clockwise rotation of the lever I8 `causes clockwise rotation of the worm I4 by the lug I9, and the valve block 28 moves with saidworm to move the face 38 of the valve block `away from the blade 56. Movement of the valve block 28 in a clockwise direction untwists the rod 46 and returns the blade 58 to its normal neutral position. If, while the rod 46 is twisted, the road resistance decreases to a point below that which causes deformation of said rod, the valve block 28 is moved by the rod in a clockwise direction relative to the blade 5|] until said rod is no longer distorted and `the blade is again in the neutral position shown in Fig. 3. It is apparent .that as the valve block 28 so moves relative to the blade 50, the ball 5I is moved off its seat by the fluid pressure in the conduit 59, groove 3|, passage 42 and the bore 49. As the ball l5I moves off its seat, the pressure in the conduits 59 and60, and on the left hand side of the piston 22 is dissipated by the,

free flow of fluid out ofthe mouth of the bore 40.

The dissipation of the pressure in the cylinder 2| at the left hand side of the piston 22 stops vthe aid to steering provided by the piston 22.

A similar action takes place when the hand wheel 55 is turned in a counterclockwise direction as viewed from the right in Fig. 1. When the road resistance to movement of the steering linkage I1 exceeds the predetermined amount which the torsion rod 4B can withstand without deformation, counterclockwise rotation of the wheel 55 causes the blade 59 to press the ball 52 onto its seat in the mouth of the bore 39. This causes fluid to ow from the pressure chamber 68 through the conduit 6I and into the cylinder 2| at the right hand side of the piston 22. Movement of the piston 22, piston rod 23, and the crosshead 25 to the left results and causes 'counterclockwise rotation of the lever I8 and the shaft I5. The counterclockwise rotation of the shaft causes counterclockwise swinging movement of the pitman arm I6 and movement of the linkage I1 to the right. As the lever I8 is rotated in ya counterclockwise direction, the worm I4 is also ne i' rotated i-n a counterclockwise direction by' the lug I9 te thereby similarly rotate the valve block 'M3E to move the face 39 away from the blade 50". Ir' while the rod 4-6 is so twisted the road resistance tofmovement oi the linkage' I1 drops below that which causes distortion of the torsion rod 46, said rod will return to its normal undeform'ed state, andl in doing so willl rotate the valve block E8 in a counterclockwise direction relative to the blade- 56 untilsaid blade is yagain inv its neutral position shown in Fig. 3. Positioning of the blade as. shown Fig. 3 permits the pressure from the conduits 61| and 62, groove 31, passage 63 andbore M to move the ball 52 on' its seat toallow fluid: to issue from theA bore MI intoI the casi-ng ZT. Thiscauses dissipation of the iluid pressures in conduitsy 6l' and 62 and in the cylinder 421 at the right hand side of the piston 22, and stops the aid to' steering provided by said piston.

FromA the foregoing it is apparent that with the use/ot the improved hydraulic steering mechani'sm, hydraulic steering aid is provided only at such. times-as when the resistance to movement of the steering linkage exceeds the torque which canffbe transmitted by the torsion rodi6v without deformation. If the steering linkage does not exerty sufficient resistance to twist the torsion rod #Siand thereby cause-oneof the balls to-'be'pressed against. its seat, the manual torque causing rotation! of the hand wheel 55 will be the only force to cause actuation of the steering linkage, and no hydraulic aid: will result. The purpose of this feature is. to allow a certain amount of road teelwto be transmitted to the driver oroperator of'. the steering wheel 55, and to thereby provide a valuable aid to a'c curate steering.

If'for any'reason the uid pressure inthe conduitsf or- B+ should fail byreason of apump failure: or for any other reason, the improved steering mechanism can still be manually steered eventhough nohydraulic steering aid is provided. Atv-suchtimes 'the piston 22 eanbe moved freely invthecylinder-121, due to the fact that there is entrapment of fluid therein. During movementof the piston iuid` can be drawn into one endithereof. throughfone or the other ofthe check valvess or 8.1-, even though one of the -balls is pressed against. itsl seat. The improved steering mechanism can always -be'operated manually and is; never locked! because of' failure of the fluidi pressuretherein.

VThe.y ballsl 5landr ttprovidefarelatively large opening, for a relatively small-movement away fronrftheir seats, .and the use of ball type valves in the improved-'steering mechanism eliminates' thewvire; draw-ing which oridinarily'occurs-in conventional fcur-way'valves wherein movement' of relativel'y. slidablei parts. causes valve lands to uncoveror-to.n closepressure porta The` improved steering4 mechanism is. adapted for use with a` wide` variety: of hydraulic steering gears and is rugged ineonstruction. It is also vapparent that partsin Figs. 5 and d which are indicatedby primed numeralsfare`v analogous to the parts of` the vprincipal form of the inventionindicate'd by the samefunprimednumerals.A y

In Fig. fthecasingsof the hydraulic ram. andcofK the control housing. 2l are; formed integral. as a Acompactsuniif` The Y hydraulic ramt 2U is provided with a cylinder 2l and with apair of spaced pistonsy 22 which are connected by means of a connecting' rod 23". The cylinder 2l' is formed with an aperture in its side wall intermediate its length, and said aperture communicates with an enclosed transversely extending chamber 8B which in turn communicates with a suitable opening 8l in the side wall of the control housing 21 adjacent one end thereof. Rotatably mounted in suitable bearings in the opposite wall portions of the chamber 8B. is a screw atl having a pinion Se fixed thereon adjacent the opening 3l. A force bar B is fixed' to an intermediate portion o the piston rod 23 and extends at a right ang-le thereto through the aperture 85 as shown. The end oi the force bar is preferably formed with an integral nut 3l which is threaded on the screw S8. The pitch of the thread on the screw 88 and in the nut 9i is sufciently steep so that the screw 83 will be rotated. by axial movement of the nut 9i.. If deI sired' the screw t8 and the nut 9i may be replaced by a` Worm and a frusto-conical follower, such as the Worm is and follower i9 of Figf.` 1, respectively. he type of nut known asv the ball nut employing ball bearings in place of conventional nut threading cooperable with a screw formed with threading for receiving said balls has also been found to be satisfactory for use as the nut 9i and the screw 8B.

Inthe mcdiiied form ofthe invention shown in 5 and 6 a control block 8 is formed with second sectoral portion 92 diametric'ally opposite the sectoral portion 3l and radially outwardly ofv the recess 36 as shown in Fig. 6. This forms axially extending faces 93 and Sift.l The block 28 is formed with threaded bores 95 and in the faces 93" and 94 respectively, as shown'. lt will be noted that in the modified form of the invention the torsion bar dll (see Fig. 2) is not used, and a' solid shaft 68" replaces the sleeve o8 oi" the principal form. The control housing il?" and the shaft d6 are substantially shorter than thehousing 2l' and the sleeve llt of theprincipal form, due to the elimination of the torsion rod'.

Referring to Fig. 6 it will be noted that the shaft d'8' is formed with a blade '91 similar to the blade 56" projecting diametrically opposite from the latter blade. An adjustable screw plug 98" is threaded into the bore 95, andv a similar screw plug lli)v is threaded into the bore 96. A compression spring i-tliis seated in the bore S95 with one end' abutting the plug a3 and has its opposite end in abutment with an angledface of the blade '9T as shown. A compression spring itil-i has one endl seated in the bore 9 in abutment with the plug' t5A and has its opposite end in abutment with the other angled surface' of the blade 57i, as shown. The compression springs le@ 'and- Hll urge the blade 9J in opposite directions and thereby tend to maintain said-'blade and the blade 5B' inthe neutral position shown. The amount of ynormal compression on the springs 400 and .itil canbe varied bly screwing the plugs 9`8 and' 99 in or out.

The. oppositeend of the control block 28' V`is formed with an integral gear to2' which meshes with the' pinion 89' extending thr'oiughI the aperture 8l. A, tubular extension 29 is formed on the. gear H12-and extends axially outwardly therefrom through a suitable bearing w3- in a. cover plate: No which closes the adjacent end of the control housing' 21.". The tubular extension 29! is: adapted tofreceivea-driven shaft t3" in keyed relationship, and said shaft may be a steering column shaft of a vehicle not otherwise having provision for hydraulic steering. The pump and valve arrangement of the modified form of the invention shown in Figs. 5 and 6 is substantially the same as that shown in Figs. l to 4. In the modified form of the invention manual steering is accomplished by turning the wheel 55v to cause simultaneous rotation therewith of the shaft 48. Blade 91, acting through springs Iil and I I, the balls 5I and 52 rotates the Valve block 28 therewith, said springs, balls 5I and 52, and shaft I3 rotating with the valve block 28 as a unit as long as the resistance to turning shaft I3 is not in excess of that force which the springs |89 and I ill can transmit without deformation. The gear H32 rotates with the valve block 28 and causes simultaneous rotation of the pinion 89 and screw 88 in the opposite direction. Rotation of the screw 88 causes axial movement therealong of the nut 9 I, and the force bar 90, piston rod 23' and pistons 22' move with the nut 9|. When the resistance to turning of the shaft I3' is such that the rotative force required to be applied thereto to overcome said resistance is in excess of that which the springs IM or I0! can withstand wihout compressive deformation thereof resulting, turning of the wheel 55', for eX- ample, in a clockwise direction as viewed from the right in Fig. 5, causes compression of the spring It! by the blade 91 and simultaneous movement of the ball 5I onto its seat by the blade 5D as the shaft 44' rotates relative to the valve block 28'.

As the ball 5I' closes the mouth of the bore fill fluid under pressure enters the left hand end of the cylinder 2| through the conduit t0 and forces the pistons 22', piston rod 23 and force bar 9B with its nut Si to the right as Viewed in'y Fig. 5.

The direction and pitch of the thread on the screw 88 is such that movement of the nut` 9| to the right thereon causes counterclockwise rota-Y tion of said screw and pinion 89. Counterclockwise rotation of the pinion 89- causes` clockwise. rotation of the gear I02 which, in turn, rotates therewith the valve block 28 and the shaft I3. Clockwise rotation of the valve block 28 moves the valve seat formed by the mouth of the bore 40' away from the ball 5I to thereby dissipate the fluid pressure in the passage 42 and conduits 59 and 63', as well as in the cylinder '2 I', thereby,

stopping the movement of the pitsons 22'. As the valve block '28 is rotated by the pistons 22', the k spring IUI is permitted to expand to its normal4 length, and the blades 5G' and 9i are returned to their normal neutral positions. if, while the spring IBI is compressed, the road resistance decreases to a point below that which caused compression of said spring, the valve block 28 is` moved by said spring in a clockwise` direction relative to the blades 5t' and Si until said spring is no longer compressed and said blades are again in the neutral position shown in Fig. 6.

When the hand wheel 55 is turned in a coun.

terclockwise direction and the road res-istance to turning of shaft i3 exceeds that which the spring I Il!) can withstand without compressionl0 shaft I 3. The blades 56 and 91 arereturned to their neutral position as the ball 52' moves olf its seat, and the spring I simultaneously expands to its normal length.

The modified form of the invention provides a compact unit by which hydraulic -steering aid can be supplied to a vehicle not otherwise having provision for hydraulic steering aid. It is apparent that when either of the balls 5I or 52 is pressed against its seat, a direct driving connection is provided between the` wheel 55 and shaft I3', and since the modified form of the invention embodies the same valve and pumping system as the principal form, manual steering is possible therewith-should the fluid pressure fail for any reason. i

Various changes and modifications mayl be made without departing from the spirit of the invention, and all of such changes are contemplated, as maycome `within the scope of the claims. f

What I claim is:

1. In a power steering mechanism: a uid pressure operated double acting ram; a first source of fluid under pressure; a second source of fluid under pressure; a unitary movable member connected to said ram and movable therewith, said movable memberbeing formed with a rst passage therein communicating with said iirst source and with one side of said ram and having a iirst bleeder opening, said movable member also being formed with a second passage therein communicating with said second source and with the other side of said ramand having a second bleeder opening; and manually operated closure means for selectively closing one of said bleeder openings to prevent the escape vof iiuid therefrom and to cause uid under pressure to enter the end of said ram communicating with said bleederl opening to move said ram, ,said movable member being connected to said ram in such a manner that said ram movement causes simultaneous movement of the closed bleeder opening in a direction away from said closure means.

2.- In a'power steering mechanism; a iiuid pressure operated double acting ram; a first source of fluid under pressure;A a second source of fluid underv pressure; a unitary movable member' con-v nected to and movable with said ram, said movable member being formed with a rst passage therein communicating with said first source and with one side of said rain and having'a first bleeder `opening, said movable member also being formed with a second passage therein communic-ating with said second source and with the other side of said ram and having a second bleeder opening; a closure member for each bleeder opening; and manually operated closure member actuating means for moving a lselected closure member into closing position over itsV bleeder opening,r to vprevent theescape of vfluid therefrom and to cause fluid under pressure to enter the end of said ram communie-ating with said bleeder opening to move said ram, saidv movable member being connected to said ram in such a manner that said ram movement lcauses simultaneous movement ofthe closed bleeder opening in a direction away from its closure member.A

e 3. In a power steering mechanism a fluid pressure operated double acting ram; a first source of fluid under pressure; a'second source of fluid under pressure; a unitary movable member con-y nected to saidramfandmovable therewith, said member being iormedwith :al iirst passage therein 4c,ommuni,eating with .said first source and with one side of said ram and having a first bleeder opening, said movable member also being for-med with a second passage therein communicating w1 h said second source and with the other side of said ram and having a second bleeder-opening spacedfrom said first bleeder opening; and manually operated means including a `member positioned between said bleeder openings for selectively closing one of said bleeder openings to prevent the escape of uid therefrom and to cause iiuid under pressure to enter the end of said vram communicatingwlth said bleeder opening to move said ram, said movable .member being connected to' said ram in such a manner that said ram movement causes simultaneous movement of the closed bleeder opening in a direction away from said closing means.

4. lin a power steering mechanism: a uid pressure operated double acting ram; a first source of uid under pressure; a second source of fluid under pressure; a unitary movable member connected to and movable with said ram, said movable member being formed with a -first passage therein communicating with said nrst source and with one side of said ram and having a nrst :bleeder opening, said movable member also being formed with a second passage therein communieating with said second source and with the other side of said ram and having a second bleeder opening spaced from and facing said first bleeder opening; a closure member for each bleeder opening.; and a manually operated member positioned between lsaid bleeder openings and between said closure members for moving a selected closure member into closing position over its bleeder opening to prevent the escape of fluid therefrom and to cause fluid under pressure to enter the end of said ram communicating with said bleeder opening to move said ram, said movable member being connected to said ram in such a manner that said ram movement causes simultaneous movement oi the closed bleeder opening in a direction away from its closure member.

5. In a power steering mechanism: a fluid pressure operated double acting ram; a iii-st source of iiuid under pressure; a second source of fluid under pressure; a unitary movable member connected to and movable with said ram, said movable member being formed with a rst passage therein communicating with said first source and with one side of said ram and having a first bleeder opening, said movable member also being formed with a second passage therein communieating with said second source and with the other side .of said ram and having a second bleeder opening spaced from and facing said first bleeder opening; a ball closure member for each bleeder opening; and a manually operated member positioned between said bleeder openings and between said balls for moving a selected ball into closing position over its bleeder opening to prevent the escape of fluid therefrom and to cause fluid under pressure to enter the end of said ram communieating with said bleeder opening to move said ram, said movable member being connected to said ram in such a manner that said ram movement causes simultaneous movement of the closed bleeder opening in a direction away from its closure member.

y 6. In a power steering mechanism: a iiuid pressure operated double acting ram; a iirst source of iiuid under pressure; a second source of iiuid under pressure; a unitary movable member connected to said ram and movable therewith, said vmovable member being formed with a rst passage therein communicating with said first source and with one side of .said ram and hawing a first bleeder opening, said movable vmember also being formed with a second passage therein communicating with `said second source and with the other lside of said ram and having a second bleeder opening; manually operated closure means including a second member normally in neutral position relative to said bleeder openings, said second member being movable away from said neutral position to cause closure of a selected one of said bleeder-openings to prevent the escape of iiuid therefrom and to cause fluid under pressure to enter the end `of said ram communieating with said bleeder opening to move said ram; and a resilient deformable member connected to said movable member and to said second member in a manner to be deformed by movement of said second member away from said neutral position. i

7. In a power steering mechanism: a fluid pressure operated double acting ram; a nrst source of uid under pressure; a second source of uid under pressure; a unitary movable member connected to and movable with said ram, said movable member being formed with a rst passage therein communicating with said first source and with one side of said ram and having a iirst bleeder opening, said movable member also being formed with a second passage therein communicating with said second source and with the other side of said ram and having a second bleeder opening; a closure member for each bleeder opening; and a manually operated-closure member actuating member normally in neutral position relative to said bleeder openings, said latter member being movable away from said neutral position to move a selected closure member into closing position over its bleeder opening to prevent the escape of fluid therefrom and to cause uid under pressure to enter the end of said ram communicating with said bleeder opening to move said ram; and a resilient deformable member connected to said unitary movable member and to said closure actuating member in a manner to be deformed by lmovement of said closure member actuating member away from said neutral position.

8. In a power steering mechanism: a fluid pressure operated double acting ram; a nrst source of iuid under pressure; a second source of uid under pressure; a rotatably mounted unitary member connected to and movable with said ram, said movable member being formed with a rst passage therein communicating with said first source and with one side of said ram and having a first bleeder opening, said rotatable member also being formed with a second passage therein communicating with said second source and with the other side of said ram and having a second bleeder opening, said rst and second bleeder openings being spaced from each other; a closure member for each bleeder opening; a manually operated closure member actuating member mounted for relative rotative movement coaxial with said rotatable member, said member being normally in neutral position relative to said bleeder openings and being rotatable away from said neutral position to move a selected closure member into closing position over its bleeder opening to prevent the escape of fluid therefrom and to cause iluid under pressure to enter the end of said ram communicating with said bleeder opening to move said ram; and atleast one spring member connected at one end to said rotatable member and connected at its other end to said actuating member in a manner to be deformed by rotation of said actuating member away from said neutral position.

` 9. In a power steering mechanism; a fluid pressure operated double acting ram; a first source of uid under pressure; a second source of uid under pressure; a rotatably mounted unitary member connected to and movable with said ram, said movable member being formed with a first passage therein communicating with said rst source and with one side of said ram and having a first bleeder opening, said rotatable member also being formed with a second passage therein communicating with said second source and with the other side of said ram and having a second bleeder opening, said first and second bleeder openings being spaced from each other; a closure member for each bleeder opening; a manually operated closure member actuating member mounted for relative rotative movement coaxial with said rotatable member and having a portion positioned between said closure members, said portion being normally in neutral position relative to said bleeder openings and being movable away from said neutral position upon rotation of said actuating member relative to said rotatable member to move a selected closure member into closing position over its bleeder opening to prevent the escape of iiuid therefrom and to cause uid under pressure to enter the end of said ram communicating with said bleeder opening to move said ram; and a torsion rod -connected at one end to said rotatable member and connected at its other end to said actuating member in a manner to be axially twisted by movement of said actuating member away from said neutral position.

10. In a power steering mechanism: a fluid pressure operated double acting ram; a first source of fluid under pressure; a second source of uid under pressure; a rotatably mounted unitary member connected to and movable with said ram, said movable member being formed with a first passage therein ycommunicating with said rst source and with one side of said ram and having a first bleeder opening, said rotatable member also being formed with a second passage therein communicating with said second source and with the other side of said ram and having a second bleeder opening, said first and second bleeder openings being spaced from each other; a closure member for each bleeder opening; a manually operated closure member actuating member mounted for relative rotative movement coaxial with said rotatable member and having a portion positioned between said closure members, said portion being normally in neutral position relative to said bleeder openings and being movable away from said neutral position, upon rotation of said actuating member relative to said rotatable member, to move a selected closure member into closing position over its bleeder opening, to prevent the escape of fluid therefrom and cause iluid under pressure to enter the end of said ram communicating with said bleeder opening, to move said ram; and a com- .pression spring connected at one end to said rotatable member and connected at its other end to said actuating member in a manner to be compressed by movement of said actuating member in one direction away from said neutral position.

11. In a power steering mechanism: a driven:

shaft; a reversible power source; mechanism for icontrolling the operation of said power source, said mechanism including: a movable first member, said power source, said first member, and said driven shaft being connected for simultaneous movement; a second member normally in neutral position relative to said first member and mounted for movement in either of two opposite directions from said neutral position, said controlling means being operable to cause said power source to drive said driven shaft and said rst member in one direction when said secondmember is moved relative to the first member a predetermined amount in said direction away from neutral position; manually operated means for moving said first member; and a resilient deformable member connected to said rst` and second members in a manner to be deformed by` trolling the operation of saidpower source, saidV mechanism including: a first member; a second member normally in neutral position relative tov said rst member and mounted for rotation a predetermined amount in either direction from said neutral position, said controlling means ,being operable to cause said power source to drive said driven shaft in one direction when said second member is rotated relative to the firstmember said predetermined amount away from neutral position; -manually operated means for rotating said rst member; and a torsion rod connected to said first and second members in a manner to be axially twisted by rotation of said firstv member away from said neutral position.

v1.3. In a power steering mechanism: a driven shaft; a double acting fluid operated ram; a source of fluid under pressure; a steeringwheel; a lost-motion steering linkage connecting said wheel with said driven shaft, said linkage including: a valve communicating with said ram and with said source for controlling the flow of uid from said source to vsaid ram, said valve, said ram, and said driven shaft being connected for simultaneous movement, and said valve having abutment means; movably mounted valve actuating means drivingly connected to said wheel and normally positioned in neutral position spaced from said abutment means, said actuating means Ibeing mounted for rotation with said wheel into engagement with said valve abutment means to provide a .direct driving connection between said wheel and said driven shaft through said valve and also providing simultaneous actuation of said valve; and a resilient deformable memberonnected to said valve and to said actuating means in a manner to be deformed by movement of said actuating means away from said neutral position.

14. In a power steering mechanism: a driven shaft; a double acting fluid operated ram; a source of lfluid under pressure; a steering wheel;

a lost-motion steering linkage connecting saidf wheel with said driven shaft, said linkage including: a valve communicating with said ram and with said source for controlling the flow of fluid from said source to said ram, said valve, said ram, and said driven shaft being connected for simultaneous movement, and said valve having abutment means; movably mounted valve actuating means drivingly connected to said wheel and normally positioned in neutral position spaced from said abutment means, said actuating mea-ns being mounted for rotation of said wheel into engagement with said valve abutment means to provide a direct driving connection be tween said wheel and said driven shaft through said valve'and also providing simultaneous actuation of said valve; and a compression spring having one end in engagement with said valve and having its other end in engagement with said actuating means in a manner to lbe com.- pressed by movement of said actuating means away from neutra-l position.

15. In a power steering mechanism: a double acting iluid operated ram drivingly connected to said driven shaft; a source of duid under pressure; a -steering wheel; a lost-motion steering linkage connecting said wheel with said driven shaft, said linkage including: a valve communieatingV with said ram and with said source for controlling the flow of fluid from said. source to said ram, said valve being drivingly connected to said driven shaft and having an abutment means; valve actuating means drivingly connected to said wheel and normally positioned in neutral position spaced from said abutment means, said actuating means being mounted for rotation with said wheel into engagement with said valve abutment means to provide a direct driving connection between said wheel and said driven shaft through said valve and simultaneous actuation of said valve; and a torsion rod fixed at one end to said valve and fixed at its other end to said actuating means in a manner to be axially twisted by rotation of said actuating means away from said neutral position.

16. In a power steering mechanism: a driven shaft; a reversible power source; a steering wheel; a lost motion steering linkage connecting said Wheel with said driven shaft, said linkage including: a control unit, said unit, said driven shaft and said source being connected for simultaneous movement, said unit also being connected to the power source in a manner to control the operation or" the latter, said unit having contact means for causing operation of said power source upon actuation oi said contact means; and movably mounted actuating means idrivingly connected to said wheel and having an abutment portion normally positioned in neutral position spaced from said Contact means, said actuating means being movable by said Wheel to move the abutment portion of said actuating means into engagement with said contact means to provide a direct driving connection between said wheel and said driven shaft through said control unit and to cause simultaneous actuation of said contact means and thereby cause operation of said power source.

1'7. In a power steering mechanism: a driven shaft; a reversible power source; mechanism for controlling the operation of said power source, said mechanism including: a movable rst member, said power source, said first member, and said driven shaft being connected for simultaneous movement; a second member normally in neutral position relative to said rst member and mounted for movement in either of two opposite directions from said neutral position, said controlling means being operable to cause said power source to drive said driven shaft and said first member in one direction when said second member is moved relative to the first member a predetermined amount in said direction away from neutral position; manually operated means for moving said rst member; and a compression spring having one end in engagement with said first member and having its other end in engagement with said second member in a position to be compressed by movement of said first member awa-y from said neutral position.

18. In a power steering mechanism: a driven shaft; a reversible power source drivingly connected to said driven shaft; mechanism for controlling tlie operation of said power source, said mechanism including: a first member; a second member normally in neutral position relative to said rst member and mounted for rotation a predetermined amount in either direction from said neutral position, said controlling means being operable to cause said power source to drive said driven shaft in one direction when said second member is rotated relative to the rst member said predetermined amount away from neutral position; manually operated means for rotating said iirst member; and a compression spring having one end in engagement with said first member and having its other end in engagement with said second member in a position to be comressed by rotation of said first member away from said neutral position.

19. In a power steering mechanism: a fluid pressure operated double acting ram; a rst source of iluid under pressure;.a rst conduit means connecting said first source to one side of said ram, said conduit means being formed with a bleeder opening; a second conduit means connecting said second source with the other side of said ram, said second conduit means also being formed with a bleeder opening; manually operated means for selectively closing one of said conduit bleeder openings to prevent the escape of iiuid therefrom and to cause uid under pressure to enter the end of said ram communicating with said bleeder opening; an inlet check valve connected to one end of said ram; and an inlet check valve connected to the other end of said ram, said check valves preventing locking of said ram during failure of said uid pressure source and closure of one of said bleeder openings.

ERVING A. PUERNER.

References Cited in the le of this patent` UNITED STATES PATENTS Number Name Date 1,896,041 McLeod Dec. 6, 1932 1,952,034 Bragg Mar. 20, 1934 2,020,951 Lemon Nov. 12. 1935 2,274,734 Esnault-Pelterie Mar. 3, 1942 2,354,992 Gottlieb Aug. 1, 1944 2,432,502 Bentley Dec, 16, 1947 2,465,761 Staude Mar. 29, 1949 2,511,660 Wilson June 13, 1950 2,554,843 Stande May 29, 1951 

